Vibratory conveyer



Oct. 5, 1937. J. A, FLlNT 2,94,785

VIBRATORY CONVEYER l V Filed June 18, 1935 5 Sheets-Sheet l VEN Tof? s James F//n 7 BY @4,M mm' Oct. 5, 1937. J. A. PUNT VIBRATORY CONVEYER Filed June 18, 1935 5 Sheets-Sheet 2 J. A. FLINT Oct. 5, 1937.

VlBRATC/RY CONEYER Filed June 18, 1935 5 SheetS-Sheet 3 v, NNN

n wh?? M FU? mm N mN Oct. 5, 1937. J. A. FLINT 2,094,785

VIBRATORY CONVEYER Filed June 18, 1935 5 Sheets-Sheet f4 TTS.

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VEA/TOR: James-H. F//H I BY Oct. 5, 1937. )q A F| |NT 2,094,785

VIBRATORY CONVEYER Filed June 18, 1935 5 SheetS-Sheet 5 ATT'Y Patented ocr. 5,1937

PATENT OFFICE VIBRATORY CONVEYER James A. Flint, Columbus, Ohio, assignor to The Traylor Vibrator Company, a corporation of Colorado Application June 18, 1935, Serial No. 27,230

4 Claims.

This invention. relates to a combined cooler and conveyer, particularly of the vibratory type.

An object of the invention is to provide a device which will simultaneously cool and convey 5 material, such as table salt, glauber salt, synthetic plastics or any granular material, whereby it may be cooled as rapidly as possible after being subjected to a heat treatment for drying said material.

Another object of the invention is to provide a very efficient cooling device which will form material of the type above mentioned into thin layers, the particles of which are constantly moving and rolling over, thereby providing a maximum surface exposure and presenting new surfaces thereof to a cooled trough in which they are contained and conveyed.

Still another object of the invention is to provide a combined cooler and conveyer whereby hot particles of material may be received at one location and transferred to another location, and during said transfer they will be sufficiently cooled to be capable of ready handling, the time and distance of travel, and thus the cooling time, being reduced to a. minimum.

Other objects of the invention will appear hereinafter, the novel features and combinations being set forth in the appended claims.

Fig. l is a side elevational view of the combined conveyer and cooler of my invention showing the discharge end thereof;

Fig. 2 is a side elevational view of the material receiving end of the device of Fig. l and, when placed end to end with Fig. 1, discloses the complete device;

Fig. 3 is a. transverse sectional view taken on the line 3 3 of Fig. 2 looking in the direction of the arrows;

Fig. 4 is a longitudinal sectional view of the vibratory motor of my invention taken on the line 4 4 of Fig. 2 looking in the direction of the arrows;

Fig. 5 is an enlarged detailed sectional View showing the mode of attaching the cover plate `to the conveyer trough or deck;

Fig. 6 is an enlarged elevational view of the device of my invention showing particularly the driving motor therefor, with part of the conveyer deck shown in section to illustrate the cooling means;

Fig. 7 is an enlarged detailed sectional view showing the supporting means for the fluid pipe and the exible attachment between said conveyer deck and said uid pipe;

Fig. 8 is a transverse sectional view similar to the view of Fig. 3 showing a modified form of conveyer trough;

Fig. 9 is a plan view of the discharge end of another modified form of a combined cooler and conveyer deck;

Fig. 10 is a side elevational view of the device of Fig. 9;

Fig. 11 is a front elevational view of the device of Figs. 9 and l0;

Fig. 12 is a transverse sectional view on the line l2-I2 of Fig. l() looking in the direction of the arrows; and

Fig. 13 is a transverse sectional View on the line |3-I3 of Fig. l0 looking in the direction of the arrows.

In a process of manufacturing numerous materials, particularly of a granular structureex amples of which are table salt, glauber salt and synthetic plastics-it is often necessary to heat the material to a relatively high temperature to remove moisture therefrom. After this heating or drying process is completed, it is often neces sary to heat the material to a relatively high temperature to remove moisture therefrom. After this heating or drying process is completed. it is necessary to cool the material before it may be easily handled or used and my invention relates to a device particularly adapted to cooling such material and for transporting it from a position where it has been subjected to the mentioned heat treatment to a position where it may be handled after being cooled.

To this end I provide the combined cooler and conveyer illustrated in the drawings comprising a vibratory deck A. Said deck A is subjected to vibratory motion by vibratory motors B which are effective to impart a conveying action to any material carried on said deck A. In the operation of said combined cooler and conveyer, hot material is fed to the deck through a chute 20 and falls into a trough 2| of said vibratory deck A. The material is then conveyed along said trough 2l where it is subjected to a cooling action, and discharged at the outlet chute 22, in a relatively cool condition, into any desired receptacle or conveyer.

The' vibratory deck A comprises the trough 2l which is substantially U-shaped in cross section, as best seen in Fig. 3. Said trough is formed by side Walls 23 connected by an arcuate bottom f Wall 24. Reinforcing side ribs 25 may be pro` vided at spaced intervals along each side of the trough 2l to increase the rigidity thereof. Spaced appreciably above the bottom wall 24 of the trough 2| is a material supporting bottom 26.

It will be evident that the material received by the chute 20 will rest on the material supporting bottom 26 and be conveyed along said bottom 26 and discharged at the outlet chute 22. Within the trough 2| and extending longitudinally thereof is a pipe or conduit 21 attached to ay source of, and adapted to carry a cooling iluid, such as water. spray nozzles 28 which are adapted to spray the cooling fluid over the lower surface of material supporting bottom 26 and adjacent the side walls 23 immediately below said material suppo-rting bottom 26. Said nozzles are preferably so spaced as to` assure the spraying of the entire area of the bottom of the material supporting bottom 26 asillustrated in Fig. 6. To this end, the spray from adjacent nozzles 28 may slightly overlap on the area covered on said material supporting bottom 26. After the cooling fluid has sprayed on the lower side of said material supporting bottom 26, it will accumulate in the bottom of the trough 2| and be carried away by the outlet 29.

The pipe 21 is supported adjacent its ends by uprights or standards 3D and 3 I, which carry adjustable brackets 32 and 33 adjacent their tops, which brackets are rigidly attached to the ends of said pipe 21, as by welding. An adjustment of the height of each end of said pipe 21 is provided by co-operating threaded rods 34 and 35 and the nuts 36 and 31. It will thus be seen that the pipe 21 is stationary and does not vibrate with the trough 2|.

To provide for the resultant relative movement between said pipe 21 and the deck A, flexible connections are provided between the trough 2| and the ends of said pipe 21. There, of course, will be similar flexible connections at each end of said pipe 21 and trough 2| and somewhat similar connections 22', 43 from deck A to outlets 22 and 29. In Fig. '1, the structure of these connections is illustrated in detail. Said structure comprises a flared sleeve 38 having an outer peripheral flange 39 adapted to be connected to the trough 2| to form a water-tight connection therewith by means of a gasket 40 and appropriate nuts and bolts 4|. The sleeve 38 has a restricted end 42 which provides a circumferential groove overwhich is adapted to be slipped one end of a flexible sleeve 43, which may be made of rubber. A retaining ring 44 is provided for attaching the flexible sleeve 43 to the end 42 of the flared sleeve 38. The other end of the ilexible sleeve 43 is attached to the pipe 21 by a retaining ringv45. It is thus seen that a fluidtight connection is provided between the pipe 21 and the trough 2| at each end thereof which allows complete freedom ofmovement of said trough 2| with respect to said pipe 21. Therefore, the vibrations of the trough 2| will not be transmitted to the pipe 21. v

It is preferred that the trough 2l be completely covered and to this end I provide a plurality of spaced standards 46 on each side of said trough 2| which carry a plurality of longitudinally extending plates 41 positioned above the trough 2|. These plates 41 are provided with downwardly extending threaded rods 48 adapted to be screwthreadedly attached to the standards 46. Clamping nuts 49 are also provided to make a rigid connection between the standards 46 and the rods 48. Adjacent the inside edge of each of the plates 41, there is provided a longitudinally extending angle member 56 which is rigidly attached to said plates 41, as by Welding.

This pipe 21 is provided with spacedA Between the angle members 50 and the top edges 5| of the trough 2|, there extends a flexible web connection 5| made of flexible material, such as canvas or rubber. This web connection not only extends along the longitudinal sides of the trough 2| but also extends across the ends thereof. Clamping plates 52 are provided to clamp the top edges of the web connection 5| to the angle members 5|] and the clamping plates 53 are provided for connecting the lower edges of the web connection 5| to the top edges 5| of the trough 2|.l Appropriate nuts and bolts may be provided for clamping the clamping plates 52 and 53 to the angle members 5D and the trough 2|, respectively. Y

A cover plate to one of the angle best seen in Fig. 5.

54 is provided which is pivoted members 50 upon hinges 55, Lifting handles 56 are provided for the cover 54 near the edge thereof removed from the hinges 55. It is thus obvious that the cover plate 54 may be pivoted about the hinges to provide access to the trough 2| but, under normal conditions, said trough will be completely closed. This prevents-contamination of the material being cooled.

As illustrated in Figs. 1 and 2 of the drawings, a plurality of vibratory motors B, of which there are two illustrated, are employed for imparting a vibratory movement to the deck A. The number of vibratory motors which will be employed will be determined by the length of the vibratory deck A and by the size thereof and thus may vary within wide limits. The vibratory motor B cornprises a base casting 51 which is of heavy construction, being made of cast iron, which casting is provided with a longitudinally extending opening 5B through which extends a plurality of spaced spring leaves or vibrator bars 59, best illustrated in Fig. 4. These spring leaves 59 are clamped adjacent their ends between bosses 66 on the base casting 51 and clamping plates 6|, by means ofy clamping screws 62. Appropriate spacers 63 are provided between each of the spring leaves 59 adjacent their clamped area. It is thus evident that each of the spring leaves 59 is mounted for free flexure.

Rigidly clamped to the center of. the spring leaves 59 is an armature shaft 64 having an opening 65 therein through which said spring leaves 59 extend. The armature shaft 64 has a boss 66 extending into the opening 65 to bear against one of the end spring leaves 59. The armature 64 on that side of the leaf spring 59, 63 opposite the boss 66 comprises a web 68 which carries a plurality of clamping screws 61 which extend through the web 68 in position to bear against a clamping plate 69 which fits against another end leaf spring 59. Appropriate spacers 16 are stacked alternately between the spring leaves 59 in alinement with the boss 66 and the clamping plate 69. It is thus evident that'r upon the screwing home of the clamping screws 61, the armature shaft 64 will be rigidly attached to the centers of the spring leaves 59 and consequently the leaf spring 59, 63, 16 resiliently connects the armature 64 to the base casting 51.

The base casting 51 is provided with a transy to the trough 2| by means of clamp bolts 16 which co-operate with appropriate brackets 11 rigid with said trough 2|. The axis of the armature shaft preferably passes through the center of percussion of the deck A or, if a plurality of motors B are employed, through the center of percussion of a selected portion of said deck A. In addition, a bracket 18 (Figs. 1 and 2) may be provided which is rigidly clamped to the trough 2| at one end by appropriate clamp bolts 19 and brackets and at the other end to the armature shaft 64 adjacent the bracket 12. If de.

sired, this bracket 18 may be omitted but I prefer to employ it so that the vibratory movement of the armature shaft 64 will be more widely distributed along the trough 2|. This bracket 18 will also make a more rigid deck construction and will reduce any tendency of buckling by said trough 2|. In addition, this additional bracket 18 reduces the static twisting moment armature shaft 64 would otherwise place on the leaf spring 59, 63 due to the static load presented by the weight of .the deck A. That is, the static moment transferred to armature shaft 64 through bracket 18 about the leaf spring 59, 63 as a fulorum will oppose the static moment transferred thereto through brackets 15, thus reducing the twisting of the leaf spring 59, 83. It may be noted that the bracket 18 may be omitted as illustrated in Fig. 6, but it is preferred to include the bracket 18 to compel the trough 2| more effectively to partake of the vibrations of the armature 64 without distortion, and for the other reasons above mentioned.

The base casting 51 is preferably flexibly supported upon standards 8|, oi' which there is one adjacent each side, which standards 8| are mounted on coil springs 82 adapted to t cupped recesses 83 in said standards 8| and to be carried adjacent their bottom end in clamp plates 84 which may be rigidly bolted to foundation 85. Due to the weight of the base casting 51, only small vibrations will be manifest therein but it is preferred that these vibrations be not transferred to the foundation 85 and thus the coil springs 82 are provided to make a flexible support for said base casting 51.

Rigidly attached to the base casting 51 is a pair of spaced U-brackets 86. Mounted upon the U-brackets 86 is a field structure for the vibratory motor B which comprises a U-shaped magnetic field core 81 preferably formed of sheet steel laminations which are carried between brackets 88 and are rigidly attached thereto by tie bolts 89. Surrounding each leg of the magnetic field core 81 is a field coil or solenoid 90 which is held in place by plate 9|, which plate 9| is mounted on the brackets 88 by tie bolts and spacers 92. The entire field assembly, comprising the U-shaped magnetic field 81, constitutes an electro-magnetic motor having spaced poles separated by air gaps from the adjacent armature 13.

The field coils 90 and the brackets 88, as well as the other parts rigidly attached thereto, are adjustably supported on the U-shaped brackets 88 by a plurality of threaded rods 93. These lthreaded rods 93 maybe adjusted with respect to the U-shaped brackets 88 to adjust the air gaps between the poles of U-shaped magnetic core 81 and the armature 13. These air gaps are so adjusted that the armature 13 and the field 81 will never come into contact with each other during operation. Clamping bolts and nuts 94 are provided for clamping the threaded rods 93 in any adjusted position, as allowed by the split condition of brackets 86.

'Ihe field coils or solenoids 90 may be connected either in series or in parallel and when energized from any source of constant frequency alternating current as, for example, ja source of commercial alternating current of 25, 30, 50 or 60 cycles, the armature 13 will be attracted to the field 81 twice during each cycle of operation and will be effectively released when the flux in the magnetic field 81 passes through zero in changing its direction. Therefore, the armature 13 will operate at a frequency of 7200 cycles per minute for a current of 60cycle frequency. The operaating frequency thereof for currents of 25, 30, 50

and 60 cycles per second will be obvious. When the armature 13 is attracted to the Afield 81, the

vspring leaves 59 will be deflected to store energy therein. When the flux in the magnetic field 8TV passes through zero or approaches zero, as aforesaid, the armature 13 will be released and the energy stored up in the spring leaves 59 will be effective to move the armature 13 away from the magnetic field 81. It is thus evident that when the field coils 90 are energized from a source of alternating current, the armature shaft 64 will be vibrated at a frequency twice the frequency of the energizing current. In order to control the amplitude of vibration of the armature 13 and thus the rate of travel of the material along the bottom 26, a variable rheostat may be placed in series or in parallel with said field coils 90.

It is also contemplated that the field coils 90 be energized simultaneously from sources of alternating current and direct current, generally termed mixed current" particularly if a frequency of 3000 or 3600 vibrations per minute is desired and the current available has a frequency` of 50 or 60 cycles per second. In practice, I never use mixed currents for frequencies of 25 or 30 cycles per second as the resulting rate of vibration is below that desired for a thoroughly fluid bed. That is, a source of direct current, such as a direct current generator, is connected in series with the field coils 90 leading to a source of alternating current. As a consequence, there will be no actual reversal of current flow in theeld coils 90 and the armature 13 will be attracted only once during each cycle of the alternating current source. Under these conditions, the armature 13 will operate at a frequency of 3600 cycles per minute where the source of alternating current is 60 cycles per second. The operating frequency of armature 13 for currents of 25, 30, 50 and 60 cycles per second will be equal to their frequency rather than twice the amount as was the condition when alternating current alone was employed. Such a system for operating a screen motor from mixed current" is disclosed in my patent for an Electric reciprocatory motor, No. 1,846,326, granted February 23, 1932.

'I'he operating frequency is preferably as high as possible and the angle of vibration of the deck, as pre-determined by the inclination of armature shaft 64, is so related to the frequency of vibration that the downward component of movement of the material supportingl boi-,tom 28 is at such a rate that any material thereon will fall at a lower rate and thus not ride as a dead load on said bottom 26. That is, the deck bottom 26 will move downwardly faster than a particle will fall, whereby particles will not ride down on the bottom 26. 'I'he bottom 26 will thus never Atrough 2| and ani7 structure carry the material as a dead load but, when moving upwardly, will strike downwardly moving particles a sharp blow, similar to a baseball bat striking a ball, and thereby throw or impel the particles through space, through which they travel in a series of hops down the bottom 26 only contacting therewith at intervals and then ony for a time sufficient to receive another blow or impulse. Where the operating frequency of the trough 2l is 7266 vibrations per minute, and the amplitude of vibration is in. the angle of inclination of the armature shaft 6d may be 10 degrees, though l degrees is a common setting. For lower frequencies, the angle must be increased to compensate therefor. It is contemplated that angles as high as 40 degrees may be employed where the lower vibrating frequencies, above mentioned, are employed. As a consequence, the natural period of vibration of the deck A. and parts rigid therewith, will be independent of the actual load thereon and will be constant at a definite value. Where lower frequencies are employed, the angle of inclination of shaft 64 will be increased to maintain this condition.

It is to be noted that the trough 2| is supported entirely from the armature shafts 64 and as they are rigidly attached to said trough 2| the vibratory movement of the armature shaft 64 will be transferred to said trough 2|. Flexible connections are, of course, provided between the which is attached thereto whereby the vibrations will be confined to said trough 2|. Said trough 2| and the armature. 13 and any parts which are rigidly attached to either therefore constitute a vibratory structure which is vibrated by the motor B. This vibratory structure will have a natural period of vibration which is determined primarily by the weight thereof and by the restoring force of the spring leaves 59. That is, the restoring force of the spring leaves 59 is so related to the weight of the vibratory structure that the natural period of vibration of said vibratory structure will be pre-determined at a desired value. In practice, it has been found to be extremely desirable to pre-determine this natural period of vibration of the vibratory structure at a frequency which is near to, but slightly different from, the frequency at which the armature '|3 of the motor is vibrated. For example, if the armature 13 is vibrated by a current having a frequency of 60 cycles per second and at a frequency of 7200 cycles per minute, the natural period of the vibratory body is preferably selected at a value slightly above or slightly below 7200 cycles per minute, for example, at '7000 or 7400 cycles per minute.

It is entirely possible, but not desirable, to operate the device by pre-determining the natural period of vibration of the vibratory structure at exactly the period of vibration of the armature 'i3 which, in the example given, would be 7260 cycles p-er minute. It has been discovered, however, that if the period of vibration of said vibratory body is in exact resonance with the frequency of vibration of the armature 13, the amplitude of vibration of the deck A will vary appreciably with the load which is placed on said deck or, in other words, with the amount of material carried on the material supporting bottom 26.

81 and causing damage to either or both if exact resonance is maintained. This is due to the fact that when a vibratory body is operating at its natural frequency the energy necessary to vibrate said body is represented only by the frictional losses thereof and there is a possibility of the amplitude of vibration becoming unduly large. However, by vibrating the vibratory structure at a period slightly different from its natural period, either above. or below the natural period, the vibrations thereof are forced and there is always a minimum amount of artificial load on said vibratory structure. This prevents any damage to the motor when the actual physical load--for example, the material carried on the bottom 'ZE- is reduced to zero. In addition, it means that the variations in the actual physical load represented by the material carried on the bottom 26 will not have a great effect upon the amplitude of vibration of the deck A. As a consequence, the amplitude of vibration of said deck A will be substantially constant regardless of the actual physical load carried on the material supporting bottom 26.

Furthermore, by operating the vibratory structure at a frequency which is near its natural period, the amount of energy necessary to vibrate said vibratory structure is very materially reduced over what it would be if said vibratory structure was not operated near its natural frequency but were operated at a frequency distantly removed therefrom. This results in a great saving in operating costs, due to the use of a small amount of current, and makes possible the employment of a motor B which is of much smaller size than would otherwise be required. It will be evident, of course, that where a plurality of motors is employed to operate a single deck A, these motors will beV operated in synchronism and in phase. Y Y

It is to be noted that the axis of vibration of the armature shaft 64 is parallel with the longitudinal axis of said shaft 64 and this axis forms an acute angle with the trough 2| and the material supporting bottom 26. This acute angle may vary between and 40 degrees and in practice is usually set at 15 or 20 degrees. This angle is very important and it is so selected that at the rate of vibration of the deck and for a minimum operating amplitude of vibration the. time of downward movement of the deck, between its extreme positions, during each oscillation, will be greater than the time the material will fall this distance. This means that the bed of materials will not operate as a dead load on the deck and will therefore not appreciably affect the natural period of vibration thereof, regardless of the actual load thereon. The natural period of operation of the deck is therefore independent of the load thereon. Due to the mode of vibration of the trough 2|, the vibratory action of the bottom 26 will have both a vertical and a horizontal com- Y ponent. The vertical component will be effective to impel the particles of material upwardly from the bottom 26 and the horizontal component will be effective to transfer said particles in the direction indicated by the arrows 95. Due to this construction, the material will therefore be effectively conveyed from the material receiving end adjacent the chute 20 to the material discharge end adjacent the chute 22.

The action of the vibratory bottom 26 on the particles of material being cooled and conveyed is particularly effective to cool said particles in a minimum of time. There are a number of reasons for this. In the first place. even though the material may be first received on the bottom 26 from the chute 20 in a pile, the vibratory action of said bottom 26 will be effective to form said material in a relatively even layer over the entire surface of the plate 26, as is illustrated in Fig. 3. This assures that the material will not travel down the bottom 26 in a pile, under which condition the inner particles would not be properly cooled. In addition, the entire mass of material effectively floats with respect to the bottom 26, as it makes contact therewith only at intervals of time for, as soon as a particle touches the bottom 26, it is immediately thrown into the air, Due to this particular action, each individual particle is spaced from each other individual particle and there is a complete absence of packing or compacting of the particles into a solid mass. The entire mass of materials is fluid-like and appears to flow somewhat like water. Not only are the individual particles slightly separated and thus exposed on their entire surface to the surrounding air but the constant impacting thereof when they strike the bottom causes them to rotate or revolvescgntinuously, insuring complete freedom of movement thereof and resulting in the contacting of first one surface area thereof and then of another surface area thereof with the cooled bottom 26. Each particle is thus turned over very frequently or continuously to present all sides thereof downwardly toward the cooled upper surface of the deck bottom 26. This combined action is very effective to cool the entire mass of particles as it is transported along the bottom 26. This action will also induce rapid evaporation of excess moisture from granular materials, which evaporation would have a cooling effect on such material.

In Fig. 8 of the drawings, I have shown a slight modification of the material supporting bottom. In this form, a material supporting bottom 96 is provided which is trough-shaped and has tapering side walls 91. It is evident that in this construction the side walls 91, as well as the bottom 96, are cooled by the direct action of the cooling fluid which issues from the nozzles 26. The construction of this form of my invention is otherwise of the type illustrated in Figs. 1 to '7, in-

clusive. This form is particularly useful if the material to be cooled is of unusually high temperature when received from the chute 20 and removes any tendency of warping of the side plates 23 when such extremely high temperature material is to be cooled.

Figs. 9, 10, 11, 12 and 13 illustrate another form of my invention. In this form of my invention there is provided a deck C having side walls 99 and a bottom wall 99. Said deck C carries a trough |00 having a material supporting bottom |0| with tapering side walls |02. Extending longitudinally from the lower surface of the bottom |0| of said trough |00, there is provided a downwardly extending flange |03. This flange preferably extends substantially the entire length of the trough |00. Projecting laterally of the deck C and between the side walls 98 thereof is a plurality of anges |04 which are attached at their tops to the trough bottom |0| and the side walls |02. The flanges |03 and |04 are effective to divide the lower surface of the bottom |0| into a plurality of separate areas.

Each of these separate areas is provided with an individual cooling means comprising an individual pipey |05 which extends into the deck C and is provided with a plurality of spray nozzles |00. of which there are two for each pipe |05, as illustrated in the drawings. It ls evident that the number of nozzles may be increased or reduced as desired. The pipes |05 are supported by brackets |01 on longitudinally extending angle members |08 and are connected by downwardly extending flexible' hose |09 to a common pipe ||0 which carries the cooling medium, such as water. If desired, individual valves may be provided for the pipes |05 whereby individual control of the sections of the trough bottom |0| is possible.

As illustrated in the drawings, a vibratory motor D, or preferably a plurality of said motors, may be provided for vibrating the deck C. It is to be understood that the motor D is essentially of the same structure as the motor B which was above described in detail. It will also be understood that the structural details of the features of the form of my invention illustrated in Figs. 9 to 13, inclusive, are essentially the same as those of the device of Figs. 1 to 7, inclusive, unless a modified structure is indicated. It will also be evident that the above described mode of operation of the device of Figs. 1 to 7, inclusive, willV also apply to the Figs. 9 to 13, inclusive.

As illustrated in the drawings, the angle members |06 are supported from the base casting of the motor D by supporting plates ||2 and by angle members I3. If desired, said angle members |00 may be supported from a foundation by standards similar to the standards 46 of Figs. l, 2 and 3. This latter method of supporting the angle members |08, with the resulting support for the pipes |05, may be preferred, for the base casting is subjected to slight vibrations.

The deck C is rigidly attached to the armature shaft |4 of the motor D by downwardly extending plates ||5 which co-operate with a T-head I6 formed integral with the armature shaft ||4. Appropriate cap screws ||1 are provided for rigidly attaching the T-head ||6 and the plates H5. The armature shaft ||4 is also provided with an upwardly extending boss ||0 which carries the bracket plates ||9 which also attach the armature shaft ||4 to the deck C. As the deck C is supported by the motor D through the armature ||4 and through the plates 5 and ||9. it will be evident that by placing plates ||9 to the rear of the leaf spring |20 of the motor D, the twisting torque on said leaf spring 20, which would be present were plates ||9 omitted, is appreciably minimized.

It will, of course, be evident that the deck C must vibrate with respect to the pipes |05 and to allow for this relative movement flexible watertight connecting means |2|, best seen in Fig. 12,`

are provided between the side walls of said deck C and said pipe |05. Clamping means of the type illustrated in detail in Fig. 7 may be here employed if desired.

It may also be mentioned that the base casting of the form of my invention illustrated in Figs. 9 to 13, inclusive, is slightly different from that of the base casting 51 of the form of Figs. 1 to 7, inclusive, in that said casting has a transversely extending groove |22, which may be seen by referring to Fig. 13. This provides for the removal of the armature shaft I4 by lifting it vertically upwardly from the base casting after leaf spring |20 is removed and provides room for the upwardly projecting boss I |8.

To review briefly the mode of operation of my invention as represented by any of the forms thereof, the material is fed to one end of the trough 2| or |00 through a chute, such as chute 20 of Fig. 2. This trough is vibrated at a very high frequency and in the case where a 60-cycle current is employed the frequency may be 7200 cycles per minute. A high frequency `of vibration is very important because of the action on the material in making it fiuid-like and constantly impacting the particles thereof to turn them over and expose all surfaces to the air and to the cooled trough bottom. In addition, the device can be operated directly from a commercial source of alternating current without requiring the inter-position of any frequency changing device, such as a motor generator set. This is of extreme practical value in reducing the initial cost. Italso eliminates all rotary machinery, thus maintaining upkeep and break-downs at a minimum.

The particles in flowing down the trough 2| or |00 will contact With the bottom 26 orl IUI which is cooled by the cooling medium which issues from the nozzles 28 or |06. Each particle of material will thereby be effectively cooled by the time it Y reaches the discharge end ofthe trough 2| or |00.

The trough A or C will be vibrated at a frequency which is near to, but not exactly equal, its natural period of vibration, whereby the amplitude of vibration thereof will be substantially constant irrespective of any variations in the physical load carried thereby and will require a relatively small amount of energy to effect a vibrating action and thus will require relatively small vibratory motors B or D. The rate of travel of the material may be controlled by a eld rheostat, beca'use by means of the latter the amplitude of vibration may be regulated.v By adjusting the rate of travel of the material, due consideration may be given to the time it must be treated to be completely cooled.

Thus material received .very hot may travel slowly over the bottom 26 while material received moderately warm may travel faster.

It is thus seen that a cooling device which also operates as a conveyor is produced which is very efficient in that it cools material in a minimum time interval and also conveys said material from a Apoint Where it has been dried or otherwise treated with heat to a point where it may be placed in receptacles or conveyors for further use.

While the bottom 26 is shown as flat, it may be corrugated to present to the material a larger cooling area for the same space. Also this construction separat'es the material intoseveral parts, each part having an inverted'triangular crosssectional area. Hence, all material is in close contact with the cooling surface.

It is also contemplated that a complementary cooling action may be realized by causing a countercurrent of air to flow over the top surface of the material. This air might be injected through chute 22 and flow out through chute 20.

In addition, without changing' the structure, hot water or steam may be `employed to heat bottom 26, in which case the device may be employed as a drier.

Obviously those skilled in the art may make various changes in the details and arrangement of parts without departing from the spirit and scope of the inv ntion as dened by the claims hereto appendee and I wish therefore not to be restricted to the precise construction herein disclosed.

Having thus described and shown an embodiaco-1,785

Aporting said deck from said base, said motor means operating to vibrate said deck with movement having both a vertical and a horizontal component of movement whereby granular materials thereon will be conveyed while the particles thereof form a fluid bed, and means for conditioning the temperature of said imperforate bottom to condition said bed.

2. In a vibratory conditioner and conveyer, the combination with a deck having an imperforate bottom lying in a generally horizontal plane, of a base, electro-magnetic vibratory notor means constructed and arranged to operate at a frequency not less than 3000 cycles per minute and including an inclined vibrator bar connected below and to said deck and to said base, said motor means operating to vibrate said deck with movement havingY both a vertical and a horizontal component of movement whereby granular materials thereon will be conveyed while the particles thereof form a fluid bed, and means for conditioning the temperature of said imperforate bottom to condition said bed.

3. In a combination cooler and conveyer, the combination with a base, of a substantially horizontal deck providing a fiat bottomed material supporting and conveying trough, means for vibrating and supporting said deck comprising a vibratory non-rotary continuous circuit electric motor constructed andarranged to vibrate said deck at a frequency not less than 3000 cycles per minute and positioned below said deck and above said base and having relatively movable parts attached respectively to said deck and base, said means being so constructed and arranged that upon operation of said motor said deck will be given a vibratory motion having both a horizontal and a vertical component of movement to convey material thereon while forming it into a fluidlike bed, and means for cooling the deck to cool the material forming'said fluid-like bed as aforesaid.

4. In a combination cooler and conveyer, the combination with a base, of a substantially horizontal deck providing a flat bottomed material supporting and conveying trough, means for vibrating said deck comprising a vibratory nonrotary continuous circuit electric motor constructed and arranged to vibrate said deck at a frequency not ,less than 3000 cycles per minute and positioned below said deck and aboveV said base and having relatively movable parts attached respectively to said deck and base, said means being so constructed and arranged that upon operation of said motor said deck will be given a vibratory motion having both a horizontal and a vertical component of movement to convey material thereon While forming it into a iiuid-like bed, and means for cooling the deck to cool the material forming said fluid-like bed as aforesaid.

f JAMES A. FLINT.

CII 

